US4783179A - Sealing device for rotary fluid machine - Google Patents

Sealing device for rotary fluid machine Download PDF

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Publication number
US4783179A
US4783179A US07/099,710 US9971087A US4783179A US 4783179 A US4783179 A US 4783179A US 9971087 A US9971087 A US 9971087A US 4783179 A US4783179 A US 4783179A
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United States
Prior art keywords
shaft
chamber
housing
bearing
seal ring
Prior art date
Legal status (The legal status is an assumption and is not a legal conclusion. Google has not performed a legal analysis and makes no representation as to the accuracy of the status listed.)
Expired - Lifetime
Application number
US07/099,710
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English (en)
Inventor
Kazuso Katayama
Yasushi Mouri
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Mitsubishi Heavy Industries Ltd
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Mitsubishi Heavy Industries Ltd
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    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F01—MACHINES OR ENGINES IN GENERAL; ENGINE PLANTS IN GENERAL; STEAM ENGINES
    • F01D—NON-POSITIVE DISPLACEMENT MACHINES OR ENGINES, e.g. STEAM TURBINES
    • F01D25/00—Component parts, details, or accessories, not provided for in, or of interest apart from, other groups
    • F01D25/18—Lubricating arrangements
    • F01D25/183—Sealing means
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C17/00—Sliding-contact bearings for exclusively rotary movement
    • F16C17/02—Sliding-contact bearings for exclusively rotary movement for radial load only
    • F16C17/03—Sliding-contact bearings for exclusively rotary movement for radial load only with tiltably-supported segments, e.g. Michell bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C27/00—Elastic or yielding bearings or bearing supports, for exclusively rotary movement
    • F16C27/02—Sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C33/00—Parts of bearings; Special methods for making bearings or parts thereof
    • F16C33/72—Sealings
    • F16C33/74—Sealings of sliding-contact bearings
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16J—PISTONS; CYLINDERS; SEALINGS
    • F16J15/00—Sealings
    • F16J15/44—Free-space packings
    • F16J15/441—Free-space packings with floating ring
    • F—MECHANICAL ENGINEERING; LIGHTING; HEATING; WEAPONS; BLASTING
    • F16—ENGINEERING ELEMENTS AND UNITS; GENERAL MEASURES FOR PRODUCING AND MAINTAINING EFFECTIVE FUNCTIONING OF MACHINES OR INSTALLATIONS; THERMAL INSULATION IN GENERAL
    • F16C—SHAFTS; FLEXIBLE SHAFTS; ELEMENTS OR CRANKSHAFT MECHANISMS; ROTARY BODIES OTHER THAN GEARING ELEMENTS; BEARINGS
    • F16C2360/00—Engines or pumps

Definitions

  • the present invention relates to a sealing device for a rotary fluid machine capable of realizing a high-speed safe drive by utilizing an oil fed to the sealing device, introducing an assembly having an additional bearing function into the sealing device, and pressing the assembly downward by the force of hydraulic pressure in order to increase the number of kinetic fulcrums from 2 in the case of a conventional bearings to 4 and to thereby heighten a safe speed of the shaft.
  • the conventional rotary fluid machine such as a compressor, an air blower and a turbine has two bearings disposed opposite end portions in a shaft chamber, and in the case of the rotary fluid machine in which a rotary shaft is provided extending through the shaft chamber, it has intensively been required to drive a long thin rotary shaft at a high speed with the intention of improving a hydrodynamic efficiency.
  • FIG. 6 is a sectional view illustrating a conventional centrifugal compressor entirely.
  • Reference numeral 1 is a shaft chamber
  • numeral 2 is a rotary shaft
  • 3 is each of bearings disposed at the opposite end portions in the shaft chamber 1
  • 4 is each seal.
  • an atmospheric side seal ring 6 and an in-chamber side seal ring 7 are disposed in a housing 5, with these rings 6, 7 separated from the shaft 2 via a small space.
  • This constitution prevents a high-pressure oil fed between both the seal rings 6, 7 from leaking out.
  • Both the seal rings 6, 7 are adapted to freely slide on inner surfaces of the housing 5 which are perpendicular to an axis of the shaft 2, in compliance with the whirling of the shaft 2. Therefore, such an oil membrane seal has no reaction force to the whirling shaft.
  • An object of the present invention is to provide a highly efficient and inexpensive high-speed rotary fluid machine in which a fluid fed into a sealing device can be utilized effectively and a safe drive can be achieved.
  • a sealing device for a rotary fluid machine having bearings which are disposed at opposite end portions in a shaft chamber and support a shaft
  • the sealing device comprising a fluid seal of a fluid having a higher pressure than in the shaft chamber, the fluid seal being provided at a portion in the shaft chamber through which the shaft extends; usual dynamic pressure type bearings disposed in the middle of the fluid sealing device itself or in the vicinity of the middle thereof, the bearings being further received in a housing of the sealing device; and sealing members for partially confining a space defined between the housing and the bearings in an axial direction and a peripheral direction in order to form a closed loop; whereby the bearings are pressed downward by a differential pressure between a pressure of the fed fluid and a pressure in the outside of the shaft chamber so as to increase the number of kinetic fulcrums for the shaft and to thereby heighten a safe speed of the shaft.
  • a bearing housing 8 is pressed downward by a differential pressure between a pressure on the periphery thereof by the high-pressure sealing oil and a pressure in an oil discharge chamber 12 which is an atmospheric pressure due to the through-hole connecting to the atmosphere.
  • an oil membrane is formed between the bearings 9 and the shaft 2. The above mentioned downward pressure is transmitted to the shaft 2 via the formed oil membrane.
  • a sealing function is given by sealing rings, and thus they have the behavior of bearings kinetically, which fact permits a high-speed safe drive.
  • FIGS. 1 to 5 are concerned with the present invention, and FIGS. 6 and 7 are in connection with a conventional technique;
  • FIG. 1 is a sectional view illustrating the constitution of a bearing portion
  • FIG. 2 is a sectional view taken along the line II--II in FIG. 1;
  • FIG. 3 is a view seen from the direction of an arrow E in FIG. 1;
  • FIG. 4a is a sectional view of another embodiment
  • FIG. 4b is a sectional view taken along the line IV--IV in FIG. 4a;
  • FIG. 5 is a sectional view of still another embodiment in which bearings are incorporated into a mechanical contact seal
  • FIG. 6 is a sectional view illustrating a conventional example entirely.
  • FIG. 7 is a sectional view of a sealing device of the device shown in FIG. 6.
  • FIG. 1 shows a newly added bearing portion in the present invention.
  • reference numeral 1 is a shaft chamber
  • numeral 4 is a housing corresponding to a housing for a sealing device of a conventional technique and is disposed along a portion of the shaft chamber 1 through which a shaft 2 extends.
  • Numerals 6 and 7 are oil membrane system seal rings having the same function as in the conventional case.
  • Numeral 8 is a bearing housing newly disposed in the present invention, and inside this housing 8, there are placed oil membrane bearings 9 usually used
  • FIG. 2 is a sectional view taken along the line II--II in FIG. 1, and the respective numerals in the former drawing indicate the same parts as in the latter drawing.
  • Reference numeral 10 represents each of extensible O-rings made from rubber or the like. Between the bearing housing 8 and the housing or seal ring housing 4, a clearance is retained so that the former 8 may be rotatable relatively to the latter 4.
  • Numeral 11 is a through-hole formed in the housing 4 and is connected to the atmosphere.
  • FIG. 1 The detail of the above mentioned structure is shown in a section view of FIG. 1 which is taken along the line III--III in FIG. 2, and in FIG. 3 seen from the direction of an arrow E in FIG. 1.
  • the O-rings 10 are disposed on an outer periphery of the bearing housing 8 exhibited in FIG. 2 so as to constitute a closed loop, as shown in FIGS. 1 and 3.
  • the high-pressure oil is fed into the housing 4 through the oil feed opening 1' lubricates the bearings 9 as the oil or fluid enters the interior of the bearing housing 8 through a fluid connection in the bearing housing 8, and acts on the atmospheric side seal ring or sealing member 6 and the in-chamber side seal ring or sealing member 7 which serve to prevent a gas in the chamber from leaking in a manner similar to a conventional concept.
  • FIGS. 4a and 4b show another embodiment in which the same principle as mentioned above is employed.
  • a bearing assembly (the housing 8 and the bearings 9) is disposed on the left side (on the atmospheric side) of the atmospheric side seal ring 6 in FIG. 4a, i.e., on the outside side of the sealing device itself.
  • the high-pressure oil having the same function as the conventional one is fed to sealing sections of the seal rings 6, 7, and is partially introduced into the oil discharge chamber 12 through the through-hole 11.
  • This oil discharge chamber 12 is a space portion defined by the bearing housing 8 and the housing 4, and a part of the space is confined by the O-rings 10 in its peripheral direction and axial direction.
  • the space sealed by the O-rings 10 retains the oil pressure from underside, and thus the high-pressure oil in the oil discharge chamber 12 lubricates the bearings 9 and simultaneously functions to downwardly press the bearing assembly including the housing 8 and the bearings 9.
  • the space portion below the O-rings 11 is entirely connected to the atmosphere, and thus the high-pressure oil passes along the atmospheric side seal ring 6 and is finally discharged through the oil discharge chamber 12 as a waste oil.
  • FIG. 5 shows another embodiment in which bearings are incorporated into a mechanical contact seal.
  • the principle of this embodiment is also identical to that described above. That is to say, the high-pressure oil fed into the housing 4 through the oil feed opening 1' lubricates the contact seal 6 and simultaneously resists an internal pressure in the shaft chamber 1 to seal the fluid in the shaft chamber 1.
  • the bearings 9 are also lubricated by the fed high-pressure oil.
  • the oil discharge chamber 12 is defined between the bearing housing 8 for supporting the bearings 9 and the housing 4, and is confined in the lower portion thereof in its peripheral direction and axial direction by the O-rings 10 in order to form the closed loop.
  • the oil discharge chamber 12 is connected to the atmosphere, and thus the chamber 12 has the atmospheric pressure therein. Under such a constitution, the bearing housing 8 is pressed downward together with the bearings 9 by a differential pressure between the pressure of the high-pressure oil and the atmospheric pressure
  • the seal ring 7 controls the leakage of the oil toward the atmospheric side of the sealing device.
  • the mechanical contact seal in which the bearing assembly can also have the function of pressing the shaft 2 downward.
  • the high-pressure oil is used as the fluid for the sealing and the lubrication, and the atmosphere is utilized as the sealing fluid having the low pressure.
  • the atmosphere is utilized as the sealing fluid having the low pressure.
  • the bearings 9 are pressed together with the bearing housing 8 downward by the above mentioned function, and the sealing is carried out by the seal rings 6, 7.
  • the seal rings 6, 7 have the behavior of the hydrodynamic bearings for the shaft 2.
  • the rotary shaft has the four fulcrums hydrodynamically, and the safe speed of the shaft 2 can thus be much more heightened on the basis of the kinetic principle than the conventional one.
  • the present invention permits the thus constituted rotary shaft to rotate at a higher speed than the conventional example
  • the function of the present invention can be utilized to allow the shaft to have a thinner and longer shape than the conventional one, because even if the shaft having such a shape is employed, the safe speed can be maintained at a high level and a high-speed safe driving is possible.

Landscapes

  • Engineering & Computer Science (AREA)
  • General Engineering & Computer Science (AREA)
  • Mechanical Engineering (AREA)
  • Physics & Mathematics (AREA)
  • Fluid Mechanics (AREA)
  • Sealing Of Bearings (AREA)
  • Sealing Using Fluids, Sealing Without Contact, And Removal Of Oil (AREA)
  • Sealing Devices (AREA)
US07/099,710 1986-03-10 1987-09-22 Sealing device for rotary fluid machine Expired - Lifetime US4783179A (en)

Applications Claiming Priority (1)

Application Number Priority Date Filing Date Title
FR8603360A FR2595430B1 (fr) 1986-03-10 1986-03-10 Dispositif d'etancheite pour machine a fluide rotative

Related Parent Applications (1)

Application Number Title Priority Date Filing Date
US06839363 Continuation 1986-03-13

Publications (1)

Publication Number Publication Date
US4783179A true US4783179A (en) 1988-11-08

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ID=9332944

Family Applications (1)

Application Number Title Priority Date Filing Date
US07/099,710 Expired - Lifetime US4783179A (en) 1986-03-10 1987-09-22 Sealing device for rotary fluid machine

Country Status (3)

Country Link
US (1) US4783179A (fr)
DE (1) DE3607703A1 (fr)
FR (1) FR2595430B1 (fr)

Cited By (13)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4992024A (en) * 1989-12-13 1991-02-12 Allied-Signal Inc. Multi-film fluid bearing damper
US5005990A (en) * 1990-04-27 1991-04-09 Ingersoll-Rand Company Pump bearing system
US5106208A (en) * 1991-04-17 1992-04-21 General Electric Company Proportioned piston ring seals
US5149206A (en) * 1991-04-17 1992-09-22 General Electric Company Hydraulic shaft damper pressure control
US5169240A (en) * 1991-04-17 1992-12-08 General Electric Company Proportioned piston ring seals
US5228784A (en) * 1991-05-16 1993-07-20 General Electric Company Squeeze film damper composite ring seal
US5651616A (en) * 1996-10-17 1997-07-29 Dresser-Rand Company Tapered bearing housing
US5738356A (en) * 1996-05-09 1998-04-14 Dresser Rand Co Shaft support structure for turbomachine
US20030063822A1 (en) * 2001-10-03 2003-04-03 Dresser-Rand Company Bearing assembly and method
US6637942B2 (en) * 2001-10-03 2003-10-28 Dresser-Rand Company Bearing assembly and method
EP1475557A1 (fr) * 2003-05-08 2004-11-10 Dresser-Rand Company Film d'huile formant un joint pour un arbre rotatif
US20090152966A1 (en) * 2007-10-11 2009-06-18 Carl Freudenberg Kg Bearing seals
US9982604B2 (en) 2015-01-20 2018-05-29 United Technologies Corporation Multi-stage inter shaft ring seal

Families Citing this family (1)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
CN112682348B (zh) * 2020-12-18 2022-08-16 山东省章丘鼓风机股份有限公司 一种胀环、主轴密封结构及风机

Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3652139A (en) * 1970-05-27 1972-03-28 United Aircraft Corp Vibration damping apparatus
US3836215A (en) * 1973-02-15 1974-09-17 Ingersoll Rand Co Shaft vibration dampening means and method
US4580911A (en) * 1984-06-22 1986-04-08 Bbc Brown, Boveri & Company, Limited Tilting-segment radial bearing

Family Cites Families (7)

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Publication number Priority date Publication date Assignee Title
CH540446A (de) * 1971-07-09 1973-08-15 Bbc Sulzer Turbomaschinen Stopbüchse für drehende Wellen
US3912342A (en) * 1974-01-09 1975-10-14 Dresser Ind Turbo-machines
US3915459A (en) * 1974-05-13 1975-10-28 Dresser Ind Turbo-machinery seal
US3989258A (en) * 1975-01-06 1976-11-02 Dresser Industries, Inc. Shaft stiffness control apparatus
US4305592A (en) * 1979-10-23 1981-12-15 Transamerica Delaval, Inc. Gas seal bushing
JPS5743017A (en) * 1980-08-27 1982-03-10 Hitachi Ltd Damping bearing
US4486024A (en) * 1983-05-17 1984-12-04 Westinghouse Electric Corp. Dual-ring gland seal for dynamoelectric machine rotor

Patent Citations (3)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US3652139A (en) * 1970-05-27 1972-03-28 United Aircraft Corp Vibration damping apparatus
US3836215A (en) * 1973-02-15 1974-09-17 Ingersoll Rand Co Shaft vibration dampening means and method
US4580911A (en) * 1984-06-22 1986-04-08 Bbc Brown, Boveri & Company, Limited Tilting-segment radial bearing

Cited By (20)

* Cited by examiner, † Cited by third party
Publication number Priority date Publication date Assignee Title
US4992024A (en) * 1989-12-13 1991-02-12 Allied-Signal Inc. Multi-film fluid bearing damper
US5005990A (en) * 1990-04-27 1991-04-09 Ingersoll-Rand Company Pump bearing system
US5106208A (en) * 1991-04-17 1992-04-21 General Electric Company Proportioned piston ring seals
US5149206A (en) * 1991-04-17 1992-09-22 General Electric Company Hydraulic shaft damper pressure control
US5169240A (en) * 1991-04-17 1992-12-08 General Electric Company Proportioned piston ring seals
US5228784A (en) * 1991-05-16 1993-07-20 General Electric Company Squeeze film damper composite ring seal
US5738356A (en) * 1996-05-09 1998-04-14 Dresser Rand Co Shaft support structure for turbomachine
US5651616A (en) * 1996-10-17 1997-07-29 Dresser-Rand Company Tapered bearing housing
WO1998016754A1 (fr) * 1996-10-17 1998-04-23 Dresser-Rand Company Boite de palier conique
US6637942B2 (en) * 2001-10-03 2003-10-28 Dresser-Rand Company Bearing assembly and method
US20030063822A1 (en) * 2001-10-03 2003-04-03 Dresser-Rand Company Bearing assembly and method
US20040156566A1 (en) * 2001-10-03 2004-08-12 Dresser-Rand Company Bearing assembly and method
US20040161180A1 (en) * 2001-10-03 2004-08-19 Dresser-Rand Company Bearing assembly and method
US7018104B2 (en) 2001-10-03 2006-03-28 Dresser-Rand Company Bearing assembly and method
US7066653B2 (en) 2001-10-03 2006-06-27 Dresser-Rand Company Bearing assembly and method
US7140109B2 (en) 2001-10-03 2006-11-28 Dresser-Rand Company Bearing assembly and method
EP1475557A1 (fr) * 2003-05-08 2004-11-10 Dresser-Rand Company Film d'huile formant un joint pour un arbre rotatif
US20040222594A1 (en) * 2003-05-08 2004-11-11 Dresser-Rand Company Oil film sealing device for a rotating shaft
US20090152966A1 (en) * 2007-10-11 2009-06-18 Carl Freudenberg Kg Bearing seals
US9982604B2 (en) 2015-01-20 2018-05-29 United Technologies Corporation Multi-stage inter shaft ring seal

Also Published As

Publication number Publication date
DE3607703A1 (de) 1987-09-17
FR2595430A1 (fr) 1987-09-11
FR2595430B1 (fr) 1989-09-15
DE3607703C2 (fr) 1989-03-23

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